US5314381A - Detent arrangement for the coupling pin of an overload element, particularly in an overload clutch - Google Patents

Detent arrangement for the coupling pin of an overload element, particularly in an overload clutch Download PDF

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Publication number
US5314381A
US5314381A US07/932,383 US93238392A US5314381A US 5314381 A US5314381 A US 5314381A US 93238392 A US93238392 A US 93238392A US 5314381 A US5314381 A US 5314381A
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United States
Prior art keywords
face
coupling pin
housing
pin
cone envelope
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Expired - Fee Related
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US07/932,383
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English (en)
Inventor
Ruprecht Maurer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Ringspann GmbH
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Ringspann GmbH
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Assigned to RINGSPANN GMBH reassignment RINGSPANN GMBH ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: MAURER, RUPRECHT
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D43/00—Automatic clutches
    • F16D43/02—Automatic clutches actuated entirely mechanically
    • F16D43/20—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure
    • F16D43/202—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure of the ratchet type
    • F16D43/204—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure of the ratchet type with intermediate balls or rollers
    • F16D43/206—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure of the ratchet type with intermediate balls or rollers moving axially between engagement and disengagement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D43/00—Automatic clutches
    • F16D43/02—Automatic clutches actuated entirely mechanically
    • F16D43/20—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure
    • F16D43/202—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure of the ratchet type
    • F16D43/2022—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure of the ratchet type with at least one part moving axially between engagement and disengagement
    • F16D43/2026—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure of the ratchet type with at least one part moving axially between engagement and disengagement with a plurality of axially moving parts

Definitions

  • the present invention relates to a detent arrangement for locking and, in the case of an overload, unlocking the coupling pin of an overload element, particularly in an overload clutch, with the front end of a coupling pin that is displaceably arranged in one clutch half being in form-locking engagement with the other clutch half. In the case of an overload, this engagement is released by the axial displacement of the coupling pin which causes it to move away from the other clutch half.
  • the rear end of the coupling pin is disposed in a housing in the one clutch half and is there provided with a detent arrangement which encloses the rear pin end with a spring arrangement whose end facing away from the other clutch half, on the one hand, is at least partially supported by the housing and, on the other hand, is supported at a collar of the coupling pin.
  • One end of the spring arrangement is supported by way of a slide ring by a plurality of locking elements that are distributed around the circumference of the coupling pin and are captured between the slide ring, a cone envelope face of the coupling pin and an essentially radially oriented contact face of the housing.
  • the coupling pin is here provided with a cone envelope face as support for the locking elements that are disposed on the side of the spring arrangement facing the other clutch half. With respect to the coupling pin, this cone envelope face extends radially outwardly toward the other clutch half.
  • This type of structure produces the result that, if the coupling pin is displaced due to an overload, the locking elements are squeezed radially outwardly against the force of the spring arrangement until the coupling pin is able to pass within and through the then outwardly displaced locking elements with a movement that is directed away from the other clutch half.
  • the problem on which the present invention is based, is solved by the present invention with a detent arrangement of the above-mentioned type in which the spring arrangement is supported in the direction toward the other clutch half by a radial shoulder of the coupling pin; the rear end of the coupling pin is provided with a radially outwardly extending cone envelope face for the locking elements, with this cone envelope face being oriented away from the other clutch half; the locking elements are supported on the contact face oriented toward the other clutch half in such a way that, if the coupling pin escapes due to an overload, the locking elements can be displaced in the direction toward the pin axis; and, in their position displaced toward the pin axis, the locking elements can be displaced parallel to the coupling pin within a housing bore surrounding the coupling pin beyond the contact face and away from the other clutch half.
  • the configuration of the detent arrangement has been changed in such a way that now, during disengagement of the clutch, the cone envelope face of the coupling pin is taken away from its contact with the locking elements so that, under the force of the spring packet, the locking elements are displaced radially inwardly toward the coupling pin and then axially within the bore together with the coupling pin.
  • This results in a stress relief for the locking elements in the course of the disengagement process and their release in the sense of the above-described movement so that the disengagement process results in only a slight, temporary increase of the pressure forces at the locking elements.
  • the result is a comparatively great reduction of the disengagement angle and the moment of response of the detent arrangement in the sense of a disengagement of the clutch without it requiring a comparable change--except for the structural configuration--in the number and type of elements employed.
  • the structure according to the invention is connected with the further advantage that now the locking elements are in the locking position on a comparatively greater circumference and move from there, for the purpose of unlocking, into a position on a smaller circumference thus improving the stressability and load-carrying capability and additionally their resistance against wear compared to the prior art arrangement in which the locking elements experience their actual supporting load on a smaller circumference from which they are then shifted to a larger circumference for unlocking.
  • the locking elements are in contact with a radially oriented annular face of the slide ring and with a cone envelope face of the housing, the latter being sloped in a direction opposite to the cone envelope face of the coupling pin.
  • the locking elements on the one hand, are in contact with a cone envelope face of the slide ring, with this cone envelope face being sloped in a direction opposite to the cone envelope face of the coupling pin and, on the other hand, with a cone envelope face of the housing, with this cone envelope face likewise being sloped in a direction opposite to the cone envelope face of the coupling pin.
  • the slope of the cone envelope face of the slide ring relative to the slope of the cone envelope face of the coupling pin is less than the slope of the cone envelope face of the housing relative to the cone envelope face of the coupling pin.
  • the locking elements are in contact with a radial contact face of the housing and with a cone envelope face of the slide ring, with these cone envelope faces being sloped in the same direction as the cone envelope face of the coupling pin but enclosing a larger angle relative to the axis of the coupling pin than the cone envelope face of the coupling pin.
  • the locking elements are in contact, on the one hand, with a cone envelope face of the housing that is sloped oppositely to the cone envelope face of the coupling pin and, on the other hand, with a cone envelope face of the slide ring which is sloped in the same sense as the cone envelope face of the coupling pin but encloses a larger angle relative to the axis of the coupling pin than the cone envelope face of the coupling pin.
  • the locking elements in the simplest case, they may be a plurality of balls that are distributed over the circumference of the coupling pin. Particularly for cases involving greater loads, however, it may be advisable to provide the locking elements in the form of ring segments that have a polygonal cross section and are distributed over the circumference of the coupling pin, with their pressure receiving side faces being parallel to the contact faces of the slide ring, the coupling pin and the housing. In the engaged case, these ring segments, must of course be arranged so as to be distributed over the circumference of the coupling pin at such intervals that they do not interfere with one another during the displacement to a smaller diameter which results when the detent arrangement is unlocked.
  • the housing is configured as a housing member that can be screwed to the one clutch half thus considerably facilitating installation.
  • the cone envelope face of the coupling pin is formed by a pin cap which is placed and screwed onto the end of the coupling pin facing away from the other clutch half.
  • pin cap, locking elements, slide ring and housing member are combined into a captive unit which can easily be unscrewed or removed as a whole in order to make the spring arrangement accessible for adjustments within the spring arrangement with respect to changing the overload moment of the detent arrangement. It is then also possible in a particularly simple manner to insert shims between the slide ring and the spring arrangement or between the spring arrangement and the shoulder of the coupling pin order to control the strength of the spring arrangement in a particularly sensitive manner.
  • the coupling pins are to be charged at their ends facing away from the second clutch half by means of a cylinder piston assembly or the like, so that a closed structural unit is formed at that end, it is advisable to configure the coupling pin in two parts in such a way that the pin shaft which accommodates the spring arrangement is releasably connected by means of screws or the like with the part of the pin facing the other clutch half and forming a shoulder at the end.
  • the pin member forming the shoulder at its end can be unscrewed so that the end of the spring arrangement becomes accessible and either a change can be made at the spring itself, which is usually composed of a packet of disk springs or to make a fine adjustment at the shims disposed on this side.
  • FIGS. 1 and 2 depict a first embodiment of a detent arrangement according to the invention in the engaged state and in the disengaged state;
  • FIGS. 3 and 4 depict a second embodiment of the detent arrangement in the engaged state and in the disengaged state
  • FIGS. 5 to 10 depict a third embodiment of the detent arrangement according to the invention showing details thereof and the conditions developing during the unlocking process;
  • FIG. 11 depicts an embodiment according to FIGS. 5 to 10 supplemented by further details
  • FIG. 12 depicts an embodiment of the detent arrangement according to the invention in conjunction with a double-action overload clutch
  • FIG. 13 depicts a modification of the embodiment of the detent arrangement according to the invention shown in FIG. 12;
  • FIG. 14 depicts a modification of the embodiment shown in FIG. 11.
  • FIG. 1 is a partial axial sectional view of an overload clutch including a clutch half 1 and a clutch half 2 which are coaxial with one another and rotatable but not axially displaceable.
  • clutch half 2 is provided with inserts 6 that are inserted into and distributed uniformly over its circumference, are fastened by means of screws 5 and are provided with indentations 7 that face clutch half 1. If the clutch is engaged, a ball 8 carried by clutch half 1 engages in each indentation 7 and thus comes in contact with the sides of indentation 7.
  • Ball 8 is disposed at the end of a coupling pin 9 where it faces clutch half 2.
  • Pin 9 is mounted so as to be displaceable within clutch half 1 parallel to the clutch axis within an insert 10.
  • the rear end of the pin is provided with a thickened portion 11 that is mounted so as to be displaceable in a housing 12 that is coaxial with pin 9 and is flanged to clutch half 1 by means of screws 13.
  • the shaft 14 of pin 9 is surrounded by a spring arrangement 15 composed of disk springs that are supported, on the side facing clutch half 2, by a collar 16 of pin 9 and on the opposite side by a slide ring 17 that is mounted on the shaft 14 of pin 9 so as to be axially displaceable and is also axially displaceably mounted within the bore of housing 12.
  • a spring arrangement 15 composed of disk springs that are supported, on the side facing clutch half 2, by a collar 16 of pin 9 and on the opposite side by a slide ring 17 that is mounted on the shaft 14 of pin 9 so as to be axially displaceable and is also axially displaceably mounted within the bore of housing 12.
  • FIG. 2 shows coupling pin 9 in its extreme right position with respect to FIG. 2 which corresponds to the unlocked position in which spring arrangement 15 is practically relaxed and ball 8 is disposed entirely within clutch half 1.
  • the described arrangement and its mode of operation practically ensures that ball 8 will be unable, during disengagement of the clutch, to strike back once more and thus cause damage to clutch half 2.
  • FIGS. 3 and 4 show the subject matter of FIGS. 1 and 2 in a somewhat modified form.
  • clutch halves 30 and 31 are provided, with, however, coupling pin 32 being provided with a tooth-shaped cutting edge 33 at its front end facing clutch half 31. When the clutch is engaged, this cutting edge enters into a corresponding tooth gap 34 formed by the insert 35 in clutch half 31 where clutch half 31 is fastened by means of screws 36.
  • coupling pin 32 facing clutch half 31 is displaceable in a housing member 37 and its rear end 38, which forms a thickened portion, is displaceable in a housing member 39 that has been screwed onto housing member 37.
  • the rear, thickened end 38 of coupling pin 32 is configured as a pin cap which is placed onto the shaft 40 of coupling pin 32 by means of a screw 41.
  • pin cap 38 again forms the cone envelope face 42 already discussed in connection with FIGS. 1 and 2 which faces the cone envelope face 43 of a slide ring 44.
  • This cone face is oriented in the same direction but encloses a larger angle relative to the pin axis.
  • Balls 45 which are uniformly distributed over the circumference of coupling pin 32 are inserted between these cone envelope faces and are supported thirdly by a radial face 46 of a hardened ring 47 that has been inserted into housing member 39.
  • the shaft 40 of coupling pin 32 is again surrounded by a spring arrangement 48 of disk springs which are supported on the side facing away from slide ring 44 by a collar 49 of coupling pin 32.
  • FIGS. 5 to 10 show a configuration that is comparable to FIGS. 3 and 4, with the reference numerals of FIGS. 3 and 4 being used again, for the sake of simplicity, for the subject matter of FIGS. 5 to 10.
  • the only difference is that the locking elements formed in FIGS. 3 and 4 by balls 45 are now formed by ring segments 51 that are distributed over the circumference of coupling pin 32. These ring segments have a polygonal cross section such that they are substantially in areal contact with the cone envelope face 42 of pin cap 38, the cone envelope face 43 of slide ring 44 and the radial contact face 46 of ring 47.
  • FIG. 6 shows how the ring segments are arranged over the circumference of coupling pin 32 when the detent arrangement is in the locking position.
  • the ring segments are noticeably spaced from one another in the circumferential direction so that, when the detent arrangement is unlocked, that is, when they move radially in the direction toward the pin axis, they do not interfere with one another.
  • FIG. 5 the torque acting between the two clutch halves 30 and 31 is illustrated by arrows 52 and 53.
  • the result of the torque are the contact pressure conditions produced between the pairing of tooth 33 and the sides of tooth gap 34 as shown by faces 54 and 55. This is applicable for normal torque transmission within the clutch.
  • FIGS. 8 and 9 are sectional views of FIG. 7 in the region of a ring segment 51.
  • FIG. 8 shows the instant at which ring segment 51 is freed from the contact face 48 of ring 47.
  • FIG. 9 shows how thereafter ring segment 51 dips into the bore 50 formed by ring 47.
  • FIG. 11 shows further details of the configuration according to FIGS. 5 to 10. While, however, the clutch in FIGS. 5, 7 and 10 is shown viewed in the radial direction, FIG. 11 is a sectional view looking at the clutch in the circumferential direction.
  • FIG. 11 is a sectional view looking at the clutch in the circumferential direction.
  • the earlier introduced reference numerals are employed correspondingly and a renewed description of the operation of the detent arrangement is therefore not considered to be necessary.
  • pin cap 38 radially inwardly passes through slide ring 44 and grips behind it by means of a radial web in the form of a spring ring 60 while on the other side, at its end facing away from the other clutch half 31, pin cap 38 is provided with a radial web 61 which is in engagement with a recess 62 on the end of housing member 39, with this recess 62 being provided only at the end of housing member 39 facing away from clutch half 31.
  • a captive, closed unit results for the group including pin cap 38, ring segments 51, slide ring 44, ring 47 and housing member 39.
  • This unit can be removed as a whole by unscrewing housing member 39 from housing member 37 and loosening screw 41 so that then spring arrangement 48 is exposed and its configuration can be changed. In the present case, for example, the number of disk springs 63 could be changed.
  • FIG. 11 also shows that coupling pin 32 is secured against rotation relative to housing member 37 by way of a feather key 65, with feather key 65 possibly having a limited play in the circumferential direction of coupling pin 32 in the manner described in German Patent 3,602,282 (corresponding to U.S. Pat. Nos. 4,798,559 and 4,838,829).
  • FIG. 12 shows the use of the subject matter of the invention in a clutch configuration according to German Unexamined Published Patent Application DE-OS 3,720,301, with the details of the detent arrangement that have been described already several times, not being repeated again.
  • a cylinder-piston assembly 73 is disposed at the housing 70 of the detent arrangement on the side facing away from the second clutch half 72.
  • the piston rod 74 of this cylinder-piston assembly is connected with coupling pin 75 so that it is possible to re-engage the detent element by charging the cylinder-piston assembly with pressure from the right side of piston 76.
  • the coupling pin is made of several parts in such a way that the pin shaft 75 which accommodates spring arrangement 48 is releasably connected by means of screws 78 or the like with the part 77 of the pin forming the shoulder 49 at its end and facing the other clutch half 72.
  • Component 77 is followed by a pin member 80 which is axially displaceably mounted in clutch half 71 and is provided at its front end, for example, with a tooth gap which engages the tooth of an intermediate pin 81 whose other end is provided with a tooth which engages in a tooth gap in side 82 of clutch half 71 where it grips around clutch half 72.
  • a pin member 80 which is axially displaceably mounted in clutch half 71 and is provided at its front end, for example, with a tooth gap which engages the tooth of an intermediate pin 81 whose other end is provided with a tooth which engages in a tooth gap in side 82 of clutch half 71 where it grips around clutch half 72.
  • FIG. 13 shows a modification of the configuration of FIG. 12 which substantially retains the reference numerals of FIG. 12.
  • This modification essentially resides in that now contact face 46 is not arranged radially as in FIG. 12 but is configured as a fluted contact face 90 so that the cone angle is oriented oppositely to the cone angle of cone envelope face 42.
  • the cone angle of cone envelope face 91 of slide ring 92 must have a slope which is inclined oppositely to the cone envelope face 42 of coupling pin 75 so that the effect described several times above is produced as intended by the present invention.
  • FIG. 14 shows a modification of the configuration of FIG. 11 with again the reference numerals employed there being continued to a substantial degree.
  • contact face 46 which is radially oriented in FIG. 11 is now configured as a cone envelope face 95 which is sloped in a direction opposite to the cone envelope face 42 of coupling pin 32.
  • cone envelope face 96 of slide ring 97 may then of course be made steeper with respect to the axis of coupling pin 32 than is the case in the embodiment according to FIG. 11.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)
  • Snaps, Bayonet Connections, Set Pins, And Snap Rings (AREA)
  • One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)
US07/932,383 1991-09-27 1992-08-19 Detent arrangement for the coupling pin of an overload element, particularly in an overload clutch Expired - Fee Related US5314381A (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE4132193 1991-09-27
DE4132193 1991-09-27
DE4134919A DE4134919A1 (de) 1991-09-27 1991-10-23 Rastanordnung fuer den schaltbolzen eines ueberlastelementes, insbesondere an einer ueberlastkupplung
DE4134919 1991-10-23

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US07/932,383 Expired - Fee Related US5314381A (en) 1991-09-27 1992-08-19 Detent arrangement for the coupling pin of an overload element, particularly in an overload clutch

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JP (1) JPH05202948A (fr)
DE (1) DE4134919A1 (fr)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2327988A (en) * 1997-08-01 1999-02-10 British Autogard Torque limiting clutch with supplementary biasing means or manual disengagement
GB2370077A (en) * 1997-08-01 2002-06-19 British Autogard Torque limiting clutch with manual disengagement means
US20070246785A1 (en) * 2006-04-20 2007-10-25 Asml Netherlands B.V. Locking device, adjustment mechanism and lithographic apparatus
US20110088818A1 (en) * 2009-10-16 2011-04-21 Long Jr Thomas F Waste Water Safety Element Torque Limiter and Method of Construction
CN102182765A (zh) * 2011-05-05 2011-09-14 西安帆力机电技术有限公司 一种钢珠脱开式转矩限制器
KR101144000B1 (ko) * 2010-02-05 2012-05-15 주식회사 리한도어 클러치
US20140073440A1 (en) * 2012-09-11 2014-03-13 Comer Industries S.P.A. Torque Limiting Device, Particularly for Power Transmission Elements
CN104455061A (zh) * 2014-12-05 2015-03-25 国家电网公司 限力矩联轴器
US20150096862A1 (en) * 2012-02-27 2015-04-09 Lo-Rez Vibration Control Ltd. Overtorque release drive
US20160242365A1 (en) * 2015-02-25 2016-08-25 Chervon (Hk) Limited Gardening tool and hedge trimmer

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DE9306193U1 (de) * 1993-04-23 1994-05-26 Chr. Mayr Gmbh + Co Kg, 87665 Mauerstetten Von außen kuppelbare, vorzugsweise automatisch kuppelbare Überlastkupplung
FR2727775A1 (fr) * 1994-12-06 1996-06-07 Burion Paul Georges Limiteur de couple
KR20030054381A (ko) * 2001-12-24 2003-07-02 주식회사 포스코 회전체의 과부하 차단장치
JP4816702B2 (ja) * 2008-09-18 2011-11-16 シンフォニアテクノロジー株式会社 防振継手
DE102010051870B4 (de) * 2010-11-22 2017-03-30 R & W Antriebselemente Gmbh Sicherheitskupplung
CN104196912B (zh) * 2013-12-27 2016-09-28 镇江恒宇传动机械有限责任公司 一种钢球式限力安全联轴器
CN108591296B (zh) * 2018-04-20 2020-07-14 苏州热工研究院有限公司 用于线缆老化检测设备的双向压力离合器

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US5005684A (en) * 1988-12-03 1991-04-09 Tsubakimoto Emerson Co. Overload clutch
US5201374A (en) * 1991-01-10 1993-04-13 Atlas Copco Tools Ab Screw joint tightening power tool

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FR1202595A (fr) * 1957-11-13 1960-01-12 Gelenkwellenbau Gmbh Accouplement élastique
US3080029A (en) * 1960-09-23 1963-03-05 Bitco Inc Overload limit clutch
US4199964A (en) * 1975-02-12 1980-04-29 Grey John C Thrust transmission or thrust producing device
US4371354A (en) * 1980-12-29 1983-02-01 Titan Tool Co. Controlled-torque apparatus
US4599019A (en) * 1983-12-20 1986-07-08 Otto Bilz, Werkzeugfabrik Overload coupling device
EP0156993A1 (fr) * 1984-01-27 1985-10-09 Christian Mayr GmbH & Co. KG Elément surcharge pour accouplements avec limiteur de couple
US4637502A (en) * 1984-01-27 1987-01-20 Christian Mayr Gmbh & Co. Kg Overload release mechanism for torque couplings
US4660247A (en) * 1985-12-31 1987-04-28 Whirlpool Corporation Temperature limiting system for a spring loaded torque limiting clutch
DE3602282A1 (de) * 1986-01-25 1987-08-20 Ringspann Maurer Kg A Ueberlastkupplung
US4798559A (en) * 1986-01-25 1989-01-17 Ringspann Albrecht Maurer Kg Automatic overload clutch structure
US4838829A (en) * 1986-01-25 1989-06-13 Ringspann Albrecht Maurer Kg Automatic overload clutch reset arrangement
US4744447A (en) * 1986-05-09 1988-05-17 Sankyo Mfg. Co., Ltd. Overload release clutch
US4896755A (en) * 1986-09-05 1990-01-30 Girguis Sobhy Labib Overload clutch
DE3720230A1 (de) * 1987-06-18 1989-01-05 Norres Geb Srimaharaj Siriwan Vorrichtung zur verbindung zweier materialbahnen
US5005684A (en) * 1988-12-03 1991-04-09 Tsubakimoto Emerson Co. Overload clutch
US5201374A (en) * 1991-01-10 1993-04-13 Atlas Copco Tools Ab Screw joint tightening power tool

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2327988A (en) * 1997-08-01 1999-02-10 British Autogard Torque limiting clutch with supplementary biasing means or manual disengagement
US6059087A (en) * 1997-08-01 2000-05-09 British Autogard Limited Of Barton Lane Torque limiting clutch
GB2327988B (en) * 1997-08-01 2002-05-15 British Autogard Torque limiting clutch
GB2370077A (en) * 1997-08-01 2002-06-19 British Autogard Torque limiting clutch with manual disengagement means
GB2370077B (en) * 1997-08-01 2002-08-14 British Autogard Torque limiting clutch
US20070246785A1 (en) * 2006-04-20 2007-10-25 Asml Netherlands B.V. Locking device, adjustment mechanism and lithographic apparatus
US20110088818A1 (en) * 2009-10-16 2011-04-21 Long Jr Thomas F Waste Water Safety Element Torque Limiter and Method of Construction
KR101144000B1 (ko) * 2010-02-05 2012-05-15 주식회사 리한도어 클러치
CN102182765A (zh) * 2011-05-05 2011-09-14 西安帆力机电技术有限公司 一种钢珠脱开式转矩限制器
US20150096862A1 (en) * 2012-02-27 2015-04-09 Lo-Rez Vibration Control Ltd. Overtorque release drive
US9255612B2 (en) * 2012-02-27 2016-02-09 Lo-Rez Vibration Control Ltd. Overtorque release drive
US20140073440A1 (en) * 2012-09-11 2014-03-13 Comer Industries S.P.A. Torque Limiting Device, Particularly for Power Transmission Elements
US8992332B2 (en) * 2012-09-11 2015-03-31 Comer Industries S.P.A. Torque limiting device, particularly for power transmission elements
CN104455061A (zh) * 2014-12-05 2015-03-25 国家电网公司 限力矩联轴器
US20160242365A1 (en) * 2015-02-25 2016-08-25 Chervon (Hk) Limited Gardening tool and hedge trimmer
US10098285B2 (en) * 2015-02-25 2018-10-16 Chervon (Hk) Limited Gardening tool and hedge trimmer

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Publication number Publication date
DE4134919A1 (de) 1993-04-08
JPH05202948A (ja) 1993-08-10
DE4134919C2 (fr) 1993-09-09

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